EP0237373B1 - Fahrzeug-Schwungrad - Google Patents

Fahrzeug-Schwungrad Download PDF

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Publication number
EP0237373B1
EP0237373B1 EP87400228A EP87400228A EP0237373B1 EP 0237373 B1 EP0237373 B1 EP 0237373B1 EP 87400228 A EP87400228 A EP 87400228A EP 87400228 A EP87400228 A EP 87400228A EP 0237373 B1 EP0237373 B1 EP 0237373B1
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EP
European Patent Office
Prior art keywords
friction
circumferential
coaxial parts
flange
support ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP87400228A
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English (en)
French (fr)
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EP0237373A1 (de
Inventor
Gustave Chasseguet
Jacques Paquin
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Valeo SE
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Valeo SE
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Publication date
Application filed by Valeo SE filed Critical Valeo SE
Publication of EP0237373A1 publication Critical patent/EP0237373A1/de
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Publication of EP0237373B1 publication Critical patent/EP0237373B1/de
Expired legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/13164—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by the supporting arrangement of the damper unit
    • F16F15/13171—Bearing arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/139—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by friction-damping means

Definitions

  • the present invention relates generally to flywheels for transmission, of the type of those usually constituting a part of inertia in clutches, in particular in clutches intended for the equipment of motor vehicles.
  • this torsion damping device is incorporated into the clutch friction disc.
  • such a damping flywheel comprises two coaxial parts mounted to rotate relative to each other, namely, in practice, a first part, which annularly, at a distance from each other, two flanges, and a second part, which, between said flanges, annularly comprises a veil, with, capable of intervening between said parts, on the one hand, elastic means with circumferential action, namely, in practice, elastic members with circumferential action, which, each individually, are arranged in housings arranged for them in said flanges, and with which are capable of interfering arms belonging to said veil, with a circumferential clearance between said elastic members and said arms, and, on the other hand, friction means.
  • these friction means are of two types.
  • friction means to which corresponds a much higher torque than the relatively moderate torque, corresponding to the preceding friction means, and which, acting in practice in series with the other components of the damping flywheel, in fact constitute a torque limiter, this torque limiter having in practice the responsibility of absorbing, by introducing a slip, any overloads liable to develop by resonance between the two coaxial parts concerned during their relative oscillations, in particular at start or stop.
  • such a torque limiter has the disadvantage of having to correspond to a torque greater than the engine torque and possibly being the source of operating incidents if it is damaged, since, acting in series, the torque to be transmitted must pass through him.
  • the present invention generally relates to a provision which, while allowing the absorption of possible overlays, is advantageously free from these drawbacks.
  • a damping flywheel for transmission in particular for a motor vehicle, of the type comprising two coaxial parts rotatably mounted with respect to each other, namely, a first part, which comprises annularly, at distance from each other, two flanges, and a second, which, between said flanges, annularly comprises a veil, with, capable of intervening between said coaxial parts, on the one hand, elastic means with circumferential action, and, on the other hand, friction means, said friction means comprising at least one friction washer slidably mounted around the axis of the assembly, this damping flywheel being generally characterized in that said washer friction is axially disposed between the web belonging to one of the coaxial parts concerned and an annular flange integral in rotation with said web, and adapted to allow, in cooperation with the latter, the i intervention of the friction means to which it belongs, and in that it is mounted to slide freely around the axis of the assembly, without there being, concomitantly, compression of the elastic
  • these friction means intervene systematically during the angular movement between the two coaxial parts concerned, beyond a certain value of this angular movement, and although the torque which corresponds to them is effectively advantageously fixed at a value less than that of the engine torque, they are able to absorb possible overtorques, then no longer acting in series with respect to the other components of the damping flywheel, and in particular elastic members with circumferential action intervening between these two coaxial parts, but in parallel to these.
  • the torque to be transmitted therefore does not pass through these friction means, it does not result in a crippling incident of operation if they happen to be the subject of any possible deterioration.
  • the friction washer used is freely sliding, its angular movement does not involve any compression of the corresponding springs, nor, therefore, any subsequent return of energy.
  • the desired amortization is advantageously faster.
  • the damping flywheel according to the invention comprises, overall, two coaxial parts A, B mounted to rotate relative to one another.
  • the part A or input part, is intended to be secured to a shaft 11, in practice a driving shaft, for example the output shaft, or crankshaft , of the engine, in the case of the equipment of a motor vehicle.
  • a driving shaft for example the output shaft, or crankshaft , of the engine, in the case of the equipment of a motor vehicle.
  • This part A comprises, annularly, around the axis of the assembly, and at a distance from each other, two flanges 12, 12 '.
  • these flanges 12, 12 By their outer periphery, or of larger diameter, these flanges 12, 12 'have substantially the same radial development, and they are secured to one another, for example by rivets 13, as shown, with insertion, between them, an annular spacer 14.
  • this annular spacer 14 has a toothing 15 at its outer periphery, and it therefore constitutes by itself a starter ring for the assembly.
  • the flanges 12, 12 'on the other hand have different radial extensions: while the flange 12 extends largely towards the axis of the assembly, the flange 12' s '' stops far away from it.
  • annular washer 16 On the internal periphery of the flange 12 is attached to the latter, on the same side as the flange 12 ', an annular washer 16, which, crossed, like said flange 12, by the screws 10, is secured to this flange 12 by these last.
  • Part B or outlet part, comprises, overall, for its part, on the one hand, a hub 18, which surrounds the washer 16 of part A, with interposition, between it and the latter, of a bearing 20 , and, on the other hand, a flange 21, which, by screws 22, is attached to said hub 18 and is thus secured in rotation to the latter.
  • the damping flywheel according to the invention is adapted to be able to serve as a reaction plate for a friction disc, not shown, and thus to be secured in rotation, by friction, to this friction disc, even though the hub of the latter is rotationally secured to a second shaft, in practice a driven shaft, for example the input shaft of a gearbox in the case, more particularly, concerned, of the equipment of a motor vehicle.
  • the bearing 20 is wedged axially between this flange 21 and a transverse shoulder 23 of the hub 18.
  • Part B also comprises, annularly, between the flanges 12, 12 ′ of part A, a web 25.
  • this veil 25 is axially pinched between the hub 18 and the flange 21, and it is secured in rotation to these by the screws 22 which connect them.
  • coaxial parts A, B thus formed are capable of intervening, on the one hand, elastic means with circumferential action, and, on the other hand, friction means.
  • these elastic circumferential action means comprise elastic circumferential action members 27 which, in practice, five in number, are each individually arranged in the housings 28 provided for them in part A, and, more precisely, in the flanges 12, 12 'which the latter comprises, these housings 28 resulting essentially from windows provided for this purpose in the middle zone of the flange 12 and notches also provided for this purpose at the internal periphery of the flange 12'.
  • the elastic members with circumferential action 27 are springs of the coil spring type, all of them elongated substantially tangentially to the same circumference of the assembly, and, at their circumferential ends, they bear. on end caps or cups 30, which are circumferentially interposed between them and the radial edges 31 of the housings 28 in which they are arranged, and which, on the side of said radial edges, each individually have, in hollow, a bowl 32 with concavity turned towards such a radial edge 31.
  • these end pieces 30 each carry, circumferentially projecting, in the embodiment shown, a pad of elastic material 33.
  • the end pieces 30 are in contact with the radial edges 31 of the housings 28, under the stress of the elastic members with circumferential action 27 which extend between them, and, possibly, these are then prestressed.
  • circumferential action elastic members 27 are capable of interfering arms 35 belonging to the web 25, these arms 35 extending radially from the latter, in the direction opposite to the axis of the assembly, being each individually arranged between two successive such elastic members with circumferential action 27.
  • the arms 35 each have two dihedral folds, of opposite orientations, so that their active part, that by which they are intended to interfere with the elastic members with circumferential action 27, extends to half distance between the flanges 12, 12 ′ of part A, in line with the middle part of said elastic members with circumferential action 27.
  • the arms 35 which the veil 25 thus comprises each have, circumferentially projecting in opposite directions relative to one another, two fingers 36T, 36R, the finger 36T extending in the supposed circumferential direction. correspond to an operation of the assembly, called “pull" operation, for which an increasing evolution of the torque transmitted develops from one of the coaxial parts A, B to the other, while the finger 36R extends in the circumferential direction opposite to the previous one, and assumed to correspond to a "retro” operation of said assembly for which the evolution of said torque is on the contrary decreasing.
  • a circumferential clearance J1 which, for the rest configuration of the assembly, is distributed in J1T, on the side of the fingers 36T, and in J1 R, on the side of the fingers 36R, the clearance J1T being in practice measured between the end of a finger 36T and the bottom of the bowl 32 of the corresponding end piece 30, while, likewise, the clearance J1 R is measured between the end of a finger 36R and the bottom of the bowl 32 of the nozzle 30 corresponding to the latter.
  • the friction means capable of intervening between the coaxial parts A, B comprise, as a corollary, in the embodiment shown, a friction washer 38, which is formed of a support washer 39 and a friction lining 40 suitably secured to this support washer 39, for example by gluing, and which, by this friction lining 40, is applied axially against a transverse shoulder 41 of the hub 18 of part B, under the stress of an elastic action washer axial 42 bearing, via a distribution washer 43, on the flange 12 belonging to part A.
  • a friction washer 38 which is formed of a support washer 39 and a friction lining 40 suitably secured to this support washer 39, for example by gluing, and which, by this friction lining 40, is applied axially against a transverse shoulder 41 of the hub 18 of part B, under the stress of an elastic action washer axial 42 bearing, via a distribution washer 43, on the flange 12 belonging to part A.
  • the elastic washer 42 is a washer of the Belleville washer type.
  • the friction means capable of intervening between the coaxial parts A, B further comprise at least one friction washer 50 axially disposed between the web 25 belonging to part B and an annular flange 51 which, integral with rotation of this web 25, extends axially away from it, between it and one of the flanges 12, 12 ′ belonging to part A, in practice the flange 12, with circumferential engagement means with clearance between said friction washer 50 and said flange 12.
  • the flange 51 thus associated with the web 25 is in one piece with the hub 18 on which this web 25 is fixed in rotation, extending, like it, radially in the direction opposite to the axis of the assembly from this hub 18.
  • the friction washer 50 consists of a support washer 52 and a friction lining 53 which is suitably secured to the support washer 52, for example by gluing, and by which it is applied against the veil 25.
  • the friction lining 53 may be free to rotate relative to the washer 55 with which it is associated, the latter then no longer being for it a support washer but a distribution washer.
  • the friction washer 50 is mounted to slide freely around the axis of the assembly.
  • a friction washer 54 which, like the washer of friction 50, is mounted to slide freely around the axis of the assembly.
  • this second friction washer 54 consists, in the embodiment shown, of a support washer 55 and of a friction lining 56, which is suitably secured to this support washer 55, for example by gluing, in this embodiment, but which, as before, can be free, and, by this friction lining 56, it is applied against the flange 1; 1
  • the friction washers 50, 54 are arranged back to back, with their support washers 52, 55 facing each other and their friction linings 53, 56 in opposite directions with respect to the other.
  • it is an elastic washer 58 of the Belleville washer type.
  • the circumferential engagement means with clearance provided between the friction washer 50 and the flange 12 of the part A comprise at least one axial tab 59, of which this friction washer 50 is integral in rotation, and a recess 60, which is formed in this flange 12, and in which is engaged, with play, said axial tab 59.
  • the axial tab 59 is integral with the support washer 52 of the friction washer 50, extending from the outer periphery thereof, and, jointly, the friction washer 54, and more precisely its support washer 55, has, at its outer periphery, at least one notch 61 by which it is in
  • friction washers 50, 54 are integral in rotation with one another.
  • the recess 60 presented by the flange 12 for an axial tab 59 of the friction washer 50 is a circularly elongated buttonhole.
  • this circumferential clearance J2 is normally distributed in J2T, on the side of the axial lugs 59 of the friction washer 50 corresponding to a "pull" operation of the assembly, and in J2R, of the opposite side, that is to say on the side corresponding to a "retro” operation of said assembly.
  • the circumferential clearance J2 is overall at least equal to that provided between the elastic members with circumferential action 27 and the arms 35 of the web 25, so that, as described below, during the angular movement between the coaxial parts A, B, and whatever the direction of evolution of this angular movement, the friction washers 50, 54 only intervene at the earliest at the same time as the said elastic members with circumferential action 27.
  • this friction torque is made less than the engine torque, but strong enough to be able to absorb any overtorque.
  • the two preceding operating phases correspond to an increasing evolution of the torque transmitted from one of the coaxial parts A, B to the other, as is for example the case when an action is exerted in this direction on the accelerator of the vehicle concerned.
  • the arms 35 of the web 25 occupy any position between the elastic circumferential members 27, and, likewise, the axial tabs 59 of the friction washers 50, 54 occupy any position between the circumferential ends of the recesses 60 of the flange 12.
  • friction washers 50, 54 being moreover freely sliding about the axis of the assembly, their intervention, in operation, is advantageously done without there being, concomitantly, compression of any of the members circumferential action elastic 27, capable of later restoring the energy which it has stored during such compression, so that the momentary unilateral angular displacement of these friction washers 50, 54, for a direction of movement of the movement between the two coaxial parts A, B concerned, does not necessarily imply their elastic return to their initial position, when the direction of development of said movement is reversed. On the contrary, the instantaneous position of these friction washers 50, 54 results from the previous operating conditions and is therefore arbitrary.
  • the friction washers 50, 54 in steady state, do not intervene before the elastic members with circumferential action 27, and the torque due to these friction washers 50, 54 therefore does not risk obliterating that due to the friction washer alone 38.
  • a single friction washer could intervene between the veil belonging to one of the coaxial parts concerned and a flange integral in rotation with this veil, and / or the axial tab provided between such a friction washer and a flange belonging to the other of said coaxial parts could come not from this friction washer but from this flange.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Pulleys (AREA)
  • Supercharger (AREA)

Claims (9)

1. Dämpfungsschwungrad für Getriebe, insbesondere für ein Kraftfahrzeug, von der Art, die zwei koaxiale Teile (A, B) enthält, welche im Verhältnis zueinander drehbeweglich angebracht sind, d.h. einen ersten Teil (A), der ringförmig zwei in einem Abstand zueinander angeordnete Flansche (12, 12') enthält, und einen zweiten Teil (B), der zwischen den genannten Flanschen (12, 12') ringförmig eine Abdeckung (25) aufweist, wobei für den Eingriff zwischen den genannten koaxialen Teilen (A, B) einerseits am Umfang wirksame elastische Mittel und andererseits Reibmittel vorgesehen sind, wobei die genannten Reibmittel wenigstens eine Reibscheibe (50) enthalten, die für eine Gleitbewegung um die Achse des Ganzen angebracht ist, dadurch gekennzeichnet, daß die genannte Reibscheibe (50) axial zwischen der Abdeckung (25), die zu einem der betreffenden koaxialen Teile (A, B) gehört, und einem ringförmigen Flansch (51) angeordnet ist, der drehbeweglich mit der genannten Abdeckung (25) verbunden ist und in Verbindung mit letzterem das Eingreifen von Reibmitteln gestattet, zu denen er gehört, und daß sie frei um die Achse des Ganzen gleitend angebracht ist, ohne daß die am Umfang wirksamen elastischen Mittel gleichzeitig zusammengedrückt würden, und mit am Umfang eingreifenden, mit Spiel versehenen Mitteln (59, 60) zwischen dieser und einem der Flansche (12, 12'), der zu dem anderen der genannten koaxialen Teile (A, B) gehört.
2. Dämpfungsschwungrad nach Anspruch 1, dadurch gekennzeichnet, daß die genannten, mit Spiel versehenen, am Umfang eingreifenden Mittel (59, 60) wenigstens eine axiale Lasche (59) enthalten, mit der die betreffende Reibscheibe (50) drehbeweglich verbunden ist, sowie eine Aussparung (60), die in einem der Flansche (12, 12') des entsprechenden koaxialen Teils (A) angebracht ist und worin die genannte axiale Lasche (59) mit Spiel eingreift.
3. Dämpfungsschwungrad nach Anspruch 2, dadurch gekennzeichnet, daß die Aussparung (60) , die der genannte Flansch (12, 12') aufweist, eine kreisförmig verlängerte längliche Aussparung ist.
4. Dämpfungsschwungrad nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß zwischen der zu einem der koaxialen Teile (A, B) gehörenden Abdeckung (25) und dem Flansch (51), der dieser zugeordnet ist, zwei Reibscheiben (50, 54) vorhanden sind, die drehbeweglich miteinander verbunden sind, und daß zwischen diesen axial wirkende elastische Mittel angeordnet sind.
5. Dämpfungsschwungrad nach Anspruch 2 und 4 in Verbindung miteinander, dadurch gekennzeichnet, daß, während die eine (50) der Reibscheiben am äußeren Umfang wenigstens eine axiale Lasche (59) aufweist, die andere (54) am äußeren Umfang wenigstens eine halbmondförmige Aussparung (61) besitzt, über die sie spielfrei mit einer solchen axialen Lasche (59) in Eingriff steht.
6. Dämpfungsschwungrad nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die zwischen den beiden koaxialen Teilen (A, B) eingesetzten, am Umfang wirksamen elastischen Mittel am Umfang wirksame elastische Organe (27) besitzen, die jeweils einzeln in Aufnahmen (28) sitzen, welche für sie im Teil (A) vorgesehen sind und mit denen zur Abdeckung (25) gehörige Arme (35) zusammenwirken können, die der Teil (B) aufweist, mit einem Umfangsspiel zwischen den genannten elastischen Organen (27) und den genannten Armen (35), und wobei das Umfangsspiel (J2) der mit Spiel versehenen Eingriffsmittel zwischen dem einen der Flansche (12, 12') des genannten Teils (A) und der Reibscheibe (50) zwischen der genannten Abdeckung (25) und einem zugehörigen Flansch (51) im wesentlichen wenigstens gleich dem Spiel (J1) ist, das zwischen den genannten elastischen Organen (27) und den genannten Armen (35) vorgesehen ist.
7. Dämpfungsschwungrad nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die am Umfang wirksamen elastischen Mittel, die zwischen den beiden koaxialen Teilen (A, B) eingesetzt sind, am Umfang wirksame elastische Organe (27) aufweisen, die jeweils einzeln in Aufnahmen (28) sitzen, die dafür im Teil (A) angebracht sind, wobei sich der Außenumfang der Reibscheibe (50) über einen Kreisumfang erstreckt, dessen Durchmesser geringer ist als derjenige des Umfangs, über den sich die genannten Aufnahmen (28) erstrecken.
8. Dämpfungsschwungrad nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß der Flansch (51) aus einem Stück mit einer Nabe (18) besteht, woran drehbar die Abdeckung (25) verkeilt ist, die sich ebenfalls radial in der der Achse des Ganzen, von dieser Nabe (18) aus gesehen, entgegengesetzten Richtung erstreckt.
9. Dämpfungsschwungrad nach Anspruch 8, dadurch gekennzeichnet, daß die Abdeckung (25) axial zwischen der Nabe (18) und einem Flansch (21) eingeklemmt ist und daß sie drehbeweglich mit dieser Nabe (18) und diesem Flansch (21) durch Schrauben (22) verbunden ist, die diese miteinander verbinden.
EP87400228A 1986-02-05 1987-02-02 Fahrzeug-Schwungrad Expired EP0237373B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8601560A FR2593871A1 (fr) 1986-02-05 1986-02-05 Volant amortisseur pour transmission, notamment pour vehicule automobile
FR8601560 1986-02-05

Publications (2)

Publication Number Publication Date
EP0237373A1 EP0237373A1 (de) 1987-09-16
EP0237373B1 true EP0237373B1 (de) 1989-12-27

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EP87400228A Expired EP0237373B1 (de) 1986-02-05 1987-02-02 Fahrzeug-Schwungrad

Country Status (5)

Country Link
US (1) US4767380A (de)
EP (1) EP0237373B1 (de)
JP (1) JPS62184261A (de)
DE (1) DE3761265D1 (de)
FR (1) FR2593871A1 (de)

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DE3743801A1 (de) * 1987-12-23 1989-07-06 Daimler Benz Ag Geteiltes schwungrad
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JPH073076Y2 (ja) * 1988-03-21 1995-01-30 アイシン精機株式会社 トルク変動吸収装置
JPH0640996Y2 (ja) * 1988-04-11 1994-10-26 株式会社大金製作所 分割型フライホイール組立体
EP0361669B1 (de) * 1988-09-28 1993-05-12 Toyota Jidosha Kabushiki Kaisha Schwungradvorrichtung mit Torsionsdämpfer
US5111714A (en) * 1989-09-11 1992-05-12 Toyota Jidosha Kabushiki Kaisha Torsional damper type flywheel device
GB2254906B (en) * 1991-01-30 1995-08-16 Automotive Products Plc A twin mass flywheel
DE4420934B4 (de) * 1993-06-19 2004-11-04 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Drehmomentübertragungseinrichtung
GB2283558B (en) * 1993-11-05 1998-03-25 Luk Lamellen & Kupplungsbau Rotary vibration damper
GB2283557B (en) * 1993-11-05 1998-03-25 Luk Lamellen & Kupplungsbau Rotary vibration damper
FR2714438B1 (fr) * 1993-12-23 1996-02-16 Valeo Amortisseur de torsion, notamment pour véhicule automobile à encombrement axial réduit.
FR2715447B1 (fr) * 1994-01-26 1996-06-07 Valeo Dispositif amortisseur de torsion, notamment pour véhicule automobile.
EP0723635B1 (de) * 1994-08-20 2001-08-01 AP TMF Limited Zweimassenschwungrad
GB2329690B (en) * 1995-03-21 1999-08-11 Automotive Products Plc A twin mass flywheel friction damping device
FR2733810B1 (fr) * 1995-05-04 1997-07-04 Valeo Amortisseur de torsion, notamment pour vehicule automobile
EP0797024B1 (de) * 1996-03-14 2005-12-21 VALEO EMBRAYAGES s.a.s. Dämpfendes Schwungrad, insbesondere für Kraftfahrzeuge
FR2746159B1 (fr) * 1996-03-14 1998-05-15 Volant amortisseur, notamment pour vehicules automobiles
EP3170686A1 (de) * 2015-11-19 2017-05-24 Sampa Otomotiv Sanayi Ve Ticaret Anonim Sirketi Kolbengehäuse für luftfeder

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Publication number Priority date Publication date Assignee Title
FR2365728A1 (fr) * 1976-09-23 1978-04-21 Ferodo Sa Dispositif amortisseur de torsion, en particulier friction d'embrayage, notamment pour vehicule automobile
JPS601497B2 (ja) * 1978-08-03 1985-01-16 アイシン精機株式会社 回転トルク伝達装置
DE3447926C2 (de) * 1983-11-15 1995-07-06 Luk Lamellen & Kupplungsbau Einrichtung zum Kompensieren von Drehstößen
DE3448510C2 (de) * 1983-11-15 1996-12-05 Luk Lamellen & Kupplungsbau Vorrichtung zum Kompensieren von Drehstößen
US4663983A (en) * 1984-07-19 1987-05-12 Aisin Seiki Kabushiki Kaisha Torque variation absorbing device

Also Published As

Publication number Publication date
FR2593871A1 (fr) 1987-08-07
EP0237373A1 (de) 1987-09-16
US4767380A (en) 1988-08-30
JPS62184261A (ja) 1987-08-12
DE3761265D1 (de) 1990-02-01

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